US20030061818A1 - Articulated heat recovery heat exchanger - Google Patents
Articulated heat recovery heat exchanger Download PDFInfo
- Publication number
- US20030061818A1 US20030061818A1 US09/968,297 US96829701A US2003061818A1 US 20030061818 A1 US20030061818 A1 US 20030061818A1 US 96829701 A US96829701 A US 96829701A US 2003061818 A1 US2003061818 A1 US 2003061818A1
- Authority
- US
- United States
- Prior art keywords
- heat exchanger
- exhaust
- exhaust flow
- flow
- compressed air
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
- F28D21/001—Recuperative heat exchangers the heat being recuperated from exhaust gases for thermal power plants or industrial processes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/70—Application in combination with
- F05D2220/76—Application in combination with an electrical generator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2280/00—Mounting arrangements; Arrangements for facilitating assembling or disassembling of heat exchanger parts
- F28F2280/10—Movable elements, e.g. being pivotable
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S165/00—Heat exchange
- Y10S165/135—Movable heat exchanger
- Y10S165/138—Partially rotable, e.g. rocking, pivoting, oscillation, tilting
Definitions
- the invention relates to an articulated heat recovery heat exchanger for use on a cogenerating recuperated microturbine to selectively heat a fluid.
- the present invention provides a cogenerating recuperated microturbine engine as well as a method for converting a recuperated microturbine into a cogenerating recuperated microturbine.
- the invention also provides an apparatus and method for selectively switching the cogenerating recuperated microturbine between a cogenerating mode and a non-cogenerating mode.
- the cogenerating recuperated microturbine engine has a recuperator with cells and spaces between the cells, an air compressor provides compressed air to the cells, and a combustor communicates with the cells to receive the compressed air.
- the combustor burns a fuel along with the compressed air to create products of combustion.
- a turbine generator communicates with the combustor and operates in response to expansion of the products of combustion to generate electricity.
- the products of combustion then flow through the turbine generator and into the spaces between the recuperator cells to preheat the compressed air.
- the products of combustion then flow out of an exhaust side of the recuperator as an exhaust flow.
- a heat exchanger is movable into and at least partially out of the exhaust flow to selectively heat a fluid in the heat exchanger.
- the microturbine engine may also include an actuator operable to move the heat exchanger into and out of the exhaust flow.
- the actuator preferably operates in response to receiving compressed air from the compressor.
- a biasing member may bias the heat exchanger toward a position either into or at least partially out of the exhaust flow.
- the microturbine engine may also include an exhaust manifold that substantially covers the exhaust side of the recuperator and receives the exhaust flow.
- the heat exchanger is located within the exhaust manifold.
- the exhaust manifold may include an intake port for receiving the exhaust flow such that the heat exchanger is movable between a first position where the heat exchanger substantially covers the intake port, and a second position where the intake port is substantially unobstructed.
- the heat exchanger may be pivotally supported near the exhaust side such that it pivots into and out of the exhaust flow about a pivot axis.
- the heat exchanger includes a fluid inlet coupling that has an inlet axis, and a fluid outlet coupling that has an outlet axis.
- the couplings are preferably configured such that the inlet and outlet axes are substantially collinear with the pivot axis.
- FIG. 1 is a perspective view of a cogenerating recuperated microturbine system embodying the present invention.
- FIG. 2 is a section view taken along line 2 - 2 of FIG. 1.
- FIG. 3 is an enlarged perspective view of the articulated heat recovery heat exchanger.
- FIG. 4 is an enlarged perspective view of the articulated heat recovery heat exchanger.
- FIG. 5 is a side view of the articulated heat recovery heat exchanger in the non-cogenerating position.
- FIG. 6 is a side view of the articulated heat recovery heat exchanger in the cogenerating position.
- FIG. 1 illustrates a microturbine system 10 including a compressor 14 , a combustion section 18 (not shown in FIG. 1), a turbine 22 , a recuperator 26 , a generator 30 , a frame 34 , a heat recovery heat exchanger 38 , and a fuel supply 40 .
- the frame 34 is constructed of steel or other known materials and should be capable of rigidly supporting the components of the system.
- the system 10 also includes an electrical cabinet 42 containing the system controls.
- the generator 30 is attached to the frame 34 and is coupled to the turbine 22 . When driven by the turbine 22 , the generator 30 produces an electrical power output at a desired voltage and frequency.
- the system 10 can use many types of known generators 30 , however permanent magnet generators are preferred. The choice of specific generators is based on the desired power output, the output characteristics (voltage and frequency), and the expected duty cycle of the equipment.
- the compressor 14 is preferably a single stage radial flow compressor of known design, driven either directly or indirectly by the turbine 22 .
- the compressor 14 pulls in atmospheric air along its central axis, and compresses the air to a pressure in the range of 3 to 5 atmospheres. From the compressor 14 , the air flows through a duct 46 to the cold side of the recuperator 26 .
- the recuperator 26 is preferably a crossflow heat exchanger having a cold gas flow path defined by a series of cells 48 within the recuperator 26 , and a hot gas flow path defined by the spaces 50 between the cells 48 of the recuperator 26 .
- the hot gas flow path receives hot combustion gasses from the turbine 22 via a diffuser section 52 and discharges them to the heat recovery heat exchanger 38 (not shown in FIG. 2).
- the cold gas flow path receives compressed air from the compressor 14 via the duct 46 .
- the compressed air is heated as it flows through the cells 48 of the recuperator 26 , finally discharging into the combustion section 18 . Preheating the combustion gas with the turbine exhaust gas before combustion results in a substantial efficiency improvement.
- combustion section 18 air and fuel are mixed. Ignition of the fuel-air mixture within the combustion chamber produces an increase in temperature and gas volume.
- the system 10 is capable of maintaining a desired power output and exhaust gas temperature. The hot exhaust gas exits the combustion section 18 and flows to the turbine 22 .
- the hot exhaust gas expands, rotating the turbine 22 , which drives the compressor 14 and the generator 30 .
- the turbine 22 is preferably a single stage radial flow turbine of known design capable of operating in the microturbine environment.
- the hot gas enters the turbine 22 at approximately 1700 F and exits at approximately 1200 F. This hot exhaust gas then flows through the diffuser section 52 to the recuperator 26 .
- the exhaust gas exits the turbine 22 at approximately 1200 F. After passing through the recuperator 26 , the exhaust gas has a temperature of approximately 420 F. This high temperature gas represents a substantial amount of thermal energy.
- microturbines simply discharged the exhaust gas into the atmosphere, wasting the associated thermal energy.
- the articulated heat recovery heat exchanger 38 provides a way to selectively heat water or other fluids by transferring a portion of the thermal energy from the hot exhaust gas to the fluid.
- the heated fluid may be used to heat potable water, or may be used in a hydronic heating system, for example.
- the microturbine therefore simultaneously generates two useful substances: electricity and heated fluid. This dual-purpose operating mode of the microturbine system 10 is termed cogeneration.
- the articulated heat recovery heat exchanger 38 (sometimes referred to herein as the “recovery unit”) includes an exhaust manifold or housing 54 , a heat exchanger 58 , a fluid inlet coupling 62 , a fluid outlet coupling 66 , an actuator 70 , and a tension spring 74 or other suitable biasing member.
- the housing 54 defines an intake opening 78 and an exhaust opening 82 and conducts the exhaust gasses expelled by the recuperator 26 from the intake opening 78 to the exhaust opening 82 where they are routed through a venting system and released to the atmosphere.
- the housing 54 includes a flange portion 86 including a plurality of holes 90 that may be used to secure the recovery unit 38 to a side of the recuperator 26 using bolts, screws, or other known fasteners.
- the housing 54 also includes a fluid drain hole 92 for the drainage of water accumulating within the housing due to condensation on the outer surfaces of the heat exchanger 58 .
- the heat exchanger 58 is of the known tube-and-fin type although other types or styles of heat exchangers are possible.
- the heat exchanger 58 is pivotally mounted within the housing 54 in a manner described in more detail below.
- the heat exchanger 58 includes a series of tubes 94 extending across the length of the heat exchanger 58 .
- the tubes 94 may be oriented in a generally serpentine fashion as illustrated in FIG. 3 or there may be multiple tubes 94 arranged in parallel extending from one end of the heat exchanger 58 to the other.
- the tubes 94 conduct fluid from one end of the heat exchanger 58 to the other, and are preferably made of aluminum, copper, stainless steel, or another suitable heat-conducting material.
- a plurality of fins 98 extends between the tubes 94 to enhance the heat transfer capacity of the heat exchanger 58 .
- the fins 98 are typically made of aluminum, copper, stainless steel, or another suitable heat-conducting material, and are brazed or otherwise thermally, structurally or metallurgically coupled to the tubes 94 .
- the fluid inlet coupling 62 defines a fluid inlet channel that has an inlet axis 106 .
- the inlet coupling 62 also includes a fixed portion 110 , communicating with a fluid source 112 (see FIG. 1), and a rotatable portion 114 communicating with the heat exchanger 58 and adapted to rotate about the inlet axis 106 .
- Relatively cold fluid is received from the fluid source 112 and conducted through the fluid inlet channel into the tubes 94 of the heat exchanger 58 .
- the fluid then flows through the tubes 94 of the heat exchanger 58 and exits the heat exchanger at the outlet coupling 66 and continues to a fluid receptacle 116 (e.g. a water heater tank or a hydronic heating system, see FIG. 1).
- a fluid receptacle 116 e.g. a water heater tank or a hydronic heating system, see FIG. 1).
- the outlet coupling 66 is similar to the inlet coupling and includes a fixed portion 118 mounted to the housing 54 and a rotatable portion 122 communicating with the heat exchanger 58 .
- the rotatable portion 122 rotates about a fluid outlet axis 126 that is substantially collinear to the inlet axis 106 .
- the couplings 62 , 66 provide rotational motion about their respective axes 106 , 126 while maintaining a fluid-tight seal between the heat exchanger 58 and the fluid source 112 and fluid receptacle 116 .
- the inlet coupling 62 and the outlet coupling 66 also serve as bearings, pivotally supporting the heat exchanger 58 for pivotal movement about a pivot axis that is substantially collinear with the inlet and outlet axes 106 , 126 .
- the actuator 70 is mounted on one end to a fixed arm 130 .
- the fixed arm 130 is mounted to the housing 54 by welding or other known fastening methods.
- the fixed arm 130 extends from one side of the housing 54 and includes a depending portion 134 to which the actuator 70 is pivotally mounted by a first pivot pin 138 .
- the other end of the actuator 70 is pivotally mounted to an actuator arm 142 by a second pivot pin 146 .
- the actuator arm 142 is fixed to the rotatable portion 114 of the inlet coupling 62 .
- the illustrated actuator 70 is a piston-cylinder type actuator having a piston 150 and a cylinder 154 , and is moveable between an extended position (FIG.
- the tension spring 74 is interconnected between the first and second pivot pins 138 , 146 and biases the actuator 70 toward the retracted position.
- the illustrated tension spring 74 is a helical spring, however other known springs such as elastic cords or bands are possible.
- the actuator 70 is operated under the influence of the compressed air from the compressor 14 , efficiency may be improved over systems using an external or dedicated electric motor to actuate the heat exchanger 58 . More specifically, to actuate the heat exchanger 58 , the illustrated construction requires only a small amount of electricity to intermittently actuate a solenoid that opens and closes a flow path for the compressed air to the cylinder 154 . Once the flow path is pressurized by the compressed air, the compressor 14 will maintain such pressure continuously until the solenoid closes the flow path. By contrast, a system using an electric motor would have to constantly supply electricity to the motor to operate against the bias of the spring 74 .
- the heat exchanger 58 is movable between a non-cogenerating, disengaged position (FIG. 5) and a cogenerating, engaged position (FIG. 6). In the disengaged position, the heat exchanger 58 is positioned substantially adjacent one of the walls of the housing 54 , allowing the exhaust gasses to enter the housing at the intake opening 78 and flow substantially unrestricted out of the housing 54 through the exhaust opening 82 .
- the heat exchanger 58 is in the disengaged position, very little exhaust gas flows across the tubes 94 and fins 98 of the heat exchanger 58 , as a result, very little heat is transferred from the exhaust gasses to the fluid flowing through the heat exchanger 58 .
- the compressed air is bled from the cylinder 154 of the actuator 70 as described above, the spring 74 then returns the actuator 70 to the retracted position, thus returning the heat exchanger 58 to the disengaged position.
Abstract
Description
- The invention relates to an articulated heat recovery heat exchanger for use on a cogenerating recuperated microturbine to selectively heat a fluid.
- The present invention provides a cogenerating recuperated microturbine engine as well as a method for converting a recuperated microturbine into a cogenerating recuperated microturbine. The invention also provides an apparatus and method for selectively switching the cogenerating recuperated microturbine between a cogenerating mode and a non-cogenerating mode. The cogenerating recuperated microturbine engine has a recuperator with cells and spaces between the cells, an air compressor provides compressed air to the cells, and a combustor communicates with the cells to receive the compressed air. The combustor burns a fuel along with the compressed air to create products of combustion. A turbine generator communicates with the combustor and operates in response to expansion of the products of combustion to generate electricity. The products of combustion then flow through the turbine generator and into the spaces between the recuperator cells to preheat the compressed air. The products of combustion then flow out of an exhaust side of the recuperator as an exhaust flow. A heat exchanger is movable into and at least partially out of the exhaust flow to selectively heat a fluid in the heat exchanger.
- The microturbine engine may also include an actuator operable to move the heat exchanger into and out of the exhaust flow. The actuator preferably operates in response to receiving compressed air from the compressor. A biasing member may bias the heat exchanger toward a position either into or at least partially out of the exhaust flow. The microturbine engine may also include an exhaust manifold that substantially covers the exhaust side of the recuperator and receives the exhaust flow. Preferably, the heat exchanger is located within the exhaust manifold. The exhaust manifold may include an intake port for receiving the exhaust flow such that the heat exchanger is movable between a first position where the heat exchanger substantially covers the intake port, and a second position where the intake port is substantially unobstructed.
- The heat exchanger may be pivotally supported near the exhaust side such that it pivots into and out of the exhaust flow about a pivot axis. Preferably, the heat exchanger includes a fluid inlet coupling that has an inlet axis, and a fluid outlet coupling that has an outlet axis. The couplings are preferably configured such that the inlet and outlet axes are substantially collinear with the pivot axis. Generally, when the heat exchanger is moved into the exhaust flow, heat is transferred from the exhaust flow to the fluid, and when the heat exchanger is moved out of the exhaust flow, a reduced amount of heat is transferred from the exhaust flow to the fluid.
- Other features and advantages of the invention will become apparent to those skilled in the art upon review of the following detailed description, claims, and drawings.
- FIG. 1 is a perspective view of a cogenerating recuperated microturbine system embodying the present invention.
- FIG. 2 is a section view taken along line2-2 of FIG. 1.
- FIG. 3 is an enlarged perspective view of the articulated heat recovery heat exchanger.
- FIG. 4 is an enlarged perspective view of the articulated heat recovery heat exchanger.
- FIG. 5 is a side view of the articulated heat recovery heat exchanger in the non-cogenerating position.
- FIG. 6 is a side view of the articulated heat recovery heat exchanger in the cogenerating position.
- Before one embodiment of the invention is explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangements of the components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced or being carried out in various ways. Also, it is understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. The use of “including” and “comprising” and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items. The use of “consisting of” and variations thereof herein is meant to encompass only the items listed thereafter. The use of letters to identify elements of a method or process is simply for identification and is not meant to indicate that the elements should be performed in a particular order.
- For the sake of brevity, not all aspects of heat exchanger and microturbine combustor technology are discussed herein. For additional description of that technology, reference is made to U.S. patent application Ser. No. 09/790,464 filed Feb. 22, 2001, Ser. No. 09/668,358 filed Sep. 25, 2000, Ser. No. 09/409,641 filed Oct. 1, 1999, Ser. No. 09/239,647 filed Jan. 29, 1999 (now U.S. Pat. No. 5,983,992), and Ser. No. 08/792,261 filed Jan. 13, 1997. The entire contents of these applications are incorporated by reference herein.
- FIG. 1 illustrates a
microturbine system 10 including acompressor 14, a combustion section 18 (not shown in FIG. 1), aturbine 22, arecuperator 26, agenerator 30, aframe 34, a heatrecovery heat exchanger 38, and afuel supply 40. - The
frame 34 is constructed of steel or other known materials and should be capable of rigidly supporting the components of the system. Thesystem 10 also includes anelectrical cabinet 42 containing the system controls. - The
generator 30 is attached to theframe 34 and is coupled to theturbine 22. When driven by theturbine 22, thegenerator 30 produces an electrical power output at a desired voltage and frequency. Thesystem 10 can use many types ofknown generators 30, however permanent magnet generators are preferred. The choice of specific generators is based on the desired power output, the output characteristics (voltage and frequency), and the expected duty cycle of the equipment. - The
compressor 14 is preferably a single stage radial flow compressor of known design, driven either directly or indirectly by theturbine 22. Thecompressor 14 pulls in atmospheric air along its central axis, and compresses the air to a pressure in the range of 3 to 5 atmospheres. From thecompressor 14, the air flows through aduct 46 to the cold side of therecuperator 26. - Referring specifically to FIG. 2, the
recuperator 26 is preferably a crossflow heat exchanger having a cold gas flow path defined by a series ofcells 48 within therecuperator 26, and a hot gas flow path defined by thespaces 50 between thecells 48 of therecuperator 26. The hot gas flow path receives hot combustion gasses from theturbine 22 via adiffuser section 52 and discharges them to the heat recovery heat exchanger 38 (not shown in FIG. 2). The cold gas flow path receives compressed air from thecompressor 14 via theduct 46. The compressed air is heated as it flows through thecells 48 of therecuperator 26, finally discharging into thecombustion section 18. Preheating the combustion gas with the turbine exhaust gas before combustion results in a substantial efficiency improvement. - In the
combustion section 18, air and fuel are mixed. Ignition of the fuel-air mixture within the combustion chamber produces an increase in temperature and gas volume. By controlling the fuel flow to thecombustion section 18, thesystem 10 is capable of maintaining a desired power output and exhaust gas temperature. The hot exhaust gas exits thecombustion section 18 and flows to theturbine 22. - Referring again to FIG. 1, in the
turbine 22, the hot exhaust gas expands, rotating theturbine 22, which drives thecompressor 14 and thegenerator 30. Theturbine 22 is preferably a single stage radial flow turbine of known design capable of operating in the microturbine environment. The hot gas enters theturbine 22 at approximately 1700 F and exits at approximately 1200 F. This hot exhaust gas then flows through thediffuser section 52 to therecuperator 26. - As mentioned above, the exhaust gas exits the
turbine 22 at approximately 1200 F. After passing through therecuperator 26, the exhaust gas has a temperature of approximately 420 F. This high temperature gas represents a substantial amount of thermal energy. Previously, microturbines simply discharged the exhaust gas into the atmosphere, wasting the associated thermal energy. The articulated heatrecovery heat exchanger 38 provides a way to selectively heat water or other fluids by transferring a portion of the thermal energy from the hot exhaust gas to the fluid. The heated fluid may be used to heat potable water, or may be used in a hydronic heating system, for example. The microturbine therefore simultaneously generates two useful substances: electricity and heated fluid. This dual-purpose operating mode of themicroturbine system 10 is termed cogeneration. - Referring now to FIGS. 3 and 4, the articulated heat recovery heat exchanger38 (sometimes referred to herein as the “recovery unit”) includes an exhaust manifold or
housing 54, aheat exchanger 58, afluid inlet coupling 62, afluid outlet coupling 66, anactuator 70, and atension spring 74 or other suitable biasing member. Thehousing 54 defines anintake opening 78 and anexhaust opening 82 and conducts the exhaust gasses expelled by therecuperator 26 from theintake opening 78 to theexhaust opening 82 where they are routed through a venting system and released to the atmosphere. Thehousing 54 includes aflange portion 86 including a plurality ofholes 90 that may be used to secure therecovery unit 38 to a side of therecuperator 26 using bolts, screws, or other known fasteners. Thehousing 54 also includes afluid drain hole 92 for the drainage of water accumulating within the housing due to condensation on the outer surfaces of theheat exchanger 58. - The
heat exchanger 58 is of the known tube-and-fin type although other types or styles of heat exchangers are possible. Theheat exchanger 58 is pivotally mounted within thehousing 54 in a manner described in more detail below. Theheat exchanger 58 includes a series oftubes 94 extending across the length of theheat exchanger 58. Thetubes 94 may be oriented in a generally serpentine fashion as illustrated in FIG. 3 or there may bemultiple tubes 94 arranged in parallel extending from one end of theheat exchanger 58 to the other. Thetubes 94 conduct fluid from one end of theheat exchanger 58 to the other, and are preferably made of aluminum, copper, stainless steel, or another suitable heat-conducting material. A plurality of fins 98 (drawn only partially in FIG. 3) extends between thetubes 94 to enhance the heat transfer capacity of theheat exchanger 58. Thefins 98 are typically made of aluminum, copper, stainless steel, or another suitable heat-conducting material, and are brazed or otherwise thermally, structurally or metallurgically coupled to thetubes 94. - The
fluid inlet coupling 62 defines a fluid inlet channel that has aninlet axis 106. Theinlet coupling 62 also includes a fixedportion 110, communicating with a fluid source 112 (see FIG. 1), and arotatable portion 114 communicating with theheat exchanger 58 and adapted to rotate about theinlet axis 106. Relatively cold fluid is received from thefluid source 112 and conducted through the fluid inlet channel into thetubes 94 of theheat exchanger 58. The fluid then flows through thetubes 94 of theheat exchanger 58 and exits the heat exchanger at theoutlet coupling 66 and continues to a fluid receptacle 116 (e.g. a water heater tank or a hydronic heating system, see FIG. 1). - The
outlet coupling 66 is similar to the inlet coupling and includes a fixedportion 118 mounted to thehousing 54 and arotatable portion 122 communicating with theheat exchanger 58. Therotatable portion 122 rotates about afluid outlet axis 126 that is substantially collinear to theinlet axis 106. Thecouplings respective axes heat exchanger 58 and thefluid source 112 andfluid receptacle 116. Theinlet coupling 62 and theoutlet coupling 66 also serve as bearings, pivotally supporting theheat exchanger 58 for pivotal movement about a pivot axis that is substantially collinear with the inlet and outlet axes 106, 126. - Referring now also to FIGS. 5 and 6, the
actuator 70 is mounted on one end to afixed arm 130. The fixedarm 130 is mounted to thehousing 54 by welding or other known fastening methods. The fixedarm 130 extends from one side of thehousing 54 and includes a dependingportion 134 to which theactuator 70 is pivotally mounted by afirst pivot pin 138. The other end of theactuator 70 is pivotally mounted to anactuator arm 142 by asecond pivot pin 146. Theactuator arm 142 is fixed to therotatable portion 114 of theinlet coupling 62. The illustratedactuator 70 is a piston-cylinder type actuator having apiston 150 and acylinder 154, and is moveable between an extended position (FIG. 6) and a retracted position (FIG. 5). Thetension spring 74 is interconnected between the first and second pivot pins 138, 146 and biases theactuator 70 toward the retracted position. The illustratedtension spring 74 is a helical spring, however other known springs such as elastic cords or bands are possible. - To move the
actuator 70 to the extended position, compressed air is bled from thecompressor 14 into thecylinder 154 of theactuator 70 by way of a high-pressure conduit 158. The pressure within thecylinder 154 creates a force on thepiston 150 of theactuator 70 that overcomes the biasing force of thespring 74 and moves theactuator 70 toward the extended position. Once in the extended position, the pressure in thecylinder 154 is maintained, preventing thespring 74 from returning theactuator 70 to the retracted position. When it is desired to return theactuator 70 to the retracted position the compressed air is bled from thecylinder 154 and the force provided by thespring 74 moves theactuator 70 back toward the retracted position. - Because the
actuator 70 is operated under the influence of the compressed air from thecompressor 14, efficiency may be improved over systems using an external or dedicated electric motor to actuate theheat exchanger 58. More specifically, to actuate theheat exchanger 58, the illustrated construction requires only a small amount of electricity to intermittently actuate a solenoid that opens and closes a flow path for the compressed air to thecylinder 154. Once the flow path is pressurized by the compressed air, thecompressor 14 will maintain such pressure continuously until the solenoid closes the flow path. By contrast, a system using an electric motor would have to constantly supply electricity to the motor to operate against the bias of thespring 74. - The
heat exchanger 58 is movable between a non-cogenerating, disengaged position (FIG. 5) and a cogenerating, engaged position (FIG. 6). In the disengaged position, theheat exchanger 58 is positioned substantially adjacent one of the walls of thehousing 54, allowing the exhaust gasses to enter the housing at theintake opening 78 and flow substantially unrestricted out of thehousing 54 through theexhaust opening 82. When theheat exchanger 58 is in the disengaged position, very little exhaust gas flows across thetubes 94 andfins 98 of theheat exchanger 58, as a result, very little heat is transferred from the exhaust gasses to the fluid flowing through theheat exchanger 58. - When it is desired to heat the fluid flowing through the
heat exchanger 58, air is bled from thecompressor 14 to move theactuator 70 toward the extended position as described above. Moving theactuator 70 toward the extended position pivots theheat exchanger 58 by way of theactuator arm 142, and positions theheat exchanger 58 in the engaged position where it substantially covers theintake opening 78. When theheat exchanger 58 is in the engaged position, substantially all of the exhaust gasses flow across thetubes 94 andfins 98 of theheat exchanger 58, transferring a maximum amount of heat from the exhaust gasses to the fluid flowing through theheat exchanger 58. After passing through theheat exchanger 58, the exhaust gasses exit thehousing 54 through theexhaust opening 82. When it is no longer desired to heat the fluid flowing through theheat exchanger 58, the compressed air is bled from thecylinder 154 of theactuator 70 as described above, thespring 74 then returns the actuator 70 to the retracted position, thus returning theheat exchanger 58 to the disengaged position. - It should be apparent that the operation of the
spring 74 andactuator 70 may be reversed such that thespring 74 biases theheat exchanger 58 toward the engaged position and theactuator 70 is used to move theheat exchanger 58 to the disengaged position. Alternatively, a dual-action actuator may be used that is capable of positively moving theheat exchanger 58 toward either position, thus eliminating the need for thespring 74.
Claims (22)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/968,297 US6598400B2 (en) | 2001-10-01 | 2001-10-01 | Gas turbine with articulated heat recovery heat exchanger |
GB0407215A GB2396661B (en) | 2001-10-01 | 2002-09-27 | Micro-turbine in combination with an articulated heat exchanger |
PCT/US2002/030831 WO2003029628A1 (en) | 2001-10-01 | 2002-09-27 | Articulated heat recovery heat exchanger |
EP02780389A EP1432893A1 (en) | 2001-10-01 | 2002-09-27 | Articulated heat recovery heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/968,297 US6598400B2 (en) | 2001-10-01 | 2001-10-01 | Gas turbine with articulated heat recovery heat exchanger |
Publications (2)
Publication Number | Publication Date |
---|---|
US20030061818A1 true US20030061818A1 (en) | 2003-04-03 |
US6598400B2 US6598400B2 (en) | 2003-07-29 |
Family
ID=25514032
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/968,297 Expired - Fee Related US6598400B2 (en) | 2001-10-01 | 2001-10-01 | Gas turbine with articulated heat recovery heat exchanger |
Country Status (4)
Country | Link |
---|---|
US (1) | US6598400B2 (en) |
EP (1) | EP1432893A1 (en) |
GB (1) | GB2396661B (en) |
WO (1) | WO2003029628A1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2408073A (en) * | 2003-11-13 | 2005-05-18 | Ingersoll Rand Energy Systems | Integral heat recovery device |
US20090249826A1 (en) * | 2005-08-15 | 2009-10-08 | Rodney Dale Hugelman | Integrated compressor/expansion engine |
WO2011139317A3 (en) * | 2009-12-31 | 2012-01-19 | Rolls-Royce North American Technologies, Inc. | Gas turbine engine and heat exchange system |
US20130011244A1 (en) * | 2010-07-29 | 2013-01-10 | General Electric Company | Reconfigurable heat transfer system for gas turbine inlet |
US20180356124A1 (en) * | 2017-06-09 | 2018-12-13 | Johnson Controls Technology Company | Movable heat exchanger |
US11609005B2 (en) | 2018-09-28 | 2023-03-21 | Johnson Controls Tyco IP Holdings LLP | Adjustable heat exchanger |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU2002951703A0 (en) * | 2002-09-27 | 2002-10-17 | Commonwealth Scientific And Industrial Research Organisation | A method and system for a combustion of methane |
WO2004099587A2 (en) * | 2003-03-24 | 2004-11-18 | Ingersoll-Rand Energy Systems Corporation | Fuel-conditioning skid |
US20050034446A1 (en) * | 2003-08-11 | 2005-02-17 | Fielder William Sheridan | Dual capture jet turbine and steam generator |
US20050115246A1 (en) * | 2003-12-01 | 2005-06-02 | Ingersoll-Rand Energy Systems Corporation | Outdoor microturbine engine having water and oil separator |
US20050120719A1 (en) * | 2003-12-08 | 2005-06-09 | Olsen Andrew J. | Internally insulated turbine assembly |
US7640751B2 (en) * | 2006-05-25 | 2010-01-05 | Siemens Energy, Inc. | Fuel heating system for turbine engines |
US7874156B2 (en) * | 2007-03-29 | 2011-01-25 | General Electric Company | Methods and apparatus for heating a fluid |
WO2009117442A2 (en) | 2008-03-17 | 2009-09-24 | Watson John D | Regenerative braking for gas turbine systems |
US7861510B1 (en) * | 2008-11-22 | 2011-01-04 | Florida Turbine Technologies, Inc. | Ceramic regenerator for a gas turbine engine |
WO2010132439A1 (en) | 2009-05-12 | 2010-11-18 | Icr Turbine Engine Corporation | Gas turbine energy storage and conversion system |
WO2011109514A1 (en) | 2010-03-02 | 2011-09-09 | Icr Turbine Engine Corporatin | Dispatchable power from a renewable energy facility |
US8984895B2 (en) | 2010-07-09 | 2015-03-24 | Icr Turbine Engine Corporation | Metallic ceramic spool for a gas turbine engine |
EP2612009B1 (en) | 2010-09-03 | 2020-04-22 | ICR Turbine Engine Corporatin | Gas turbine engine |
US9051873B2 (en) | 2011-05-20 | 2015-06-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine shaft attachment |
WO2013059586A1 (en) | 2011-10-20 | 2013-04-25 | Icr Turbine Engine Corporation | Multi-fuel service station |
US10094288B2 (en) | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
US20140125070A1 (en) * | 2012-11-08 | 2014-05-08 | Caterpillar Sarl | Cooling package latch mechanism |
US20170219246A1 (en) * | 2016-01-29 | 2017-08-03 | Reese Price | Heat Extractor to Capture and Recycle Heat Energy within a Furnace |
US10921015B2 (en) * | 2018-08-28 | 2021-02-16 | Johnson Controls Technology Company | Systems and methods for adjustment of heat exchanger position |
CN112944968A (en) * | 2021-01-08 | 2021-06-11 | 徐亮红 | Water pipe waste heat utilization device |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2147283A (en) * | 1938-01-19 | 1939-02-14 | Hart & Cooley Mfg Company | Heating device |
US2914917A (en) * | 1956-11-09 | 1959-12-01 | Gen Electric | Control of heat supply to heat recovery boiler of regenerative cycle gas turbine powerplant |
US2994509A (en) * | 1959-04-10 | 1961-08-01 | Curtiss Wright Corp | Variable area turbine nozzle |
US3584459A (en) * | 1968-09-12 | 1971-06-15 | Gen Motors Corp | Gas turbine engine with combustion chamber bypass for fuel-air ratio control and turbine cooling |
DE2733931B2 (en) | 1977-07-27 | 1979-08-23 | Kraftwerk Union Ag, 4330 Muelheim | Gas turbine system with a heat exchanger downstream of the gas turbine for waste heat recovery |
FR2616212B1 (en) | 1987-06-04 | 1990-04-20 | Valeo | HOT AIR VENTILATION AND HEATING DEVICE WITH PIVOTING RADIATOR |
DE19541889A1 (en) | 1995-11-10 | 1997-05-15 | Asea Brown Boveri | Power plant |
UA41470C2 (en) | 1996-02-01 | 2001-09-17 | Норсен Рісерч Енд Інжінірінг Корпорейшн | Separate element of heat exchanger (versions), heat exchanger with plate ribs, method for assemblage of separate elements of heat exchanger, method for assemblage of heat exchanger |
DE19911645A1 (en) | 1999-03-16 | 2000-09-21 | Volkswagen Ag | Heating device for heating up air flow includes a heat exchanger in various heating positions able to swivel into an air current to be heated up. |
US6484799B1 (en) * | 1999-03-29 | 2002-11-26 | John T. Irish | Control system for movable heat recovery coils |
US20020035830A1 (en) | 2000-02-23 | 2002-03-28 | Karl Fleer | Reversible recuperator |
-
2001
- 2001-10-01 US US09/968,297 patent/US6598400B2/en not_active Expired - Fee Related
-
2002
- 2002-09-27 WO PCT/US2002/030831 patent/WO2003029628A1/en not_active Application Discontinuation
- 2002-09-27 GB GB0407215A patent/GB2396661B/en not_active Expired - Fee Related
- 2002-09-27 EP EP02780389A patent/EP1432893A1/en not_active Withdrawn
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2408073A (en) * | 2003-11-13 | 2005-05-18 | Ingersoll Rand Energy Systems | Integral heat recovery device |
FR2862345A1 (en) * | 2003-11-13 | 2005-05-20 | Ingersoll Rand Energy Systems | HEAT EXCHANGE DEVICE AND METHOD FOR CONTROLLING THE TEMPERATURE OF A FLUID, ESPECIALLY FOR A MICROTURBINE ENGINE |
US20050144931A1 (en) * | 2003-11-13 | 2005-07-07 | Floyd Stephen M. | Integral heat recovery device |
US20090249826A1 (en) * | 2005-08-15 | 2009-10-08 | Rodney Dale Hugelman | Integrated compressor/expansion engine |
US7841205B2 (en) * | 2005-08-15 | 2010-11-30 | Whitemoss, Inc. | Integrated compressor/expansion engine |
WO2011139317A3 (en) * | 2009-12-31 | 2012-01-19 | Rolls-Royce North American Technologies, Inc. | Gas turbine engine and heat exchange system |
US8910465B2 (en) | 2009-12-31 | 2014-12-16 | Rolls-Royce North American Technologies, Inc. | Gas turbine engine and heat exchange system |
US20130011244A1 (en) * | 2010-07-29 | 2013-01-10 | General Electric Company | Reconfigurable heat transfer system for gas turbine inlet |
US20180356124A1 (en) * | 2017-06-09 | 2018-12-13 | Johnson Controls Technology Company | Movable heat exchanger |
US11609005B2 (en) | 2018-09-28 | 2023-03-21 | Johnson Controls Tyco IP Holdings LLP | Adjustable heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
GB2396661A (en) | 2004-06-30 |
GB0407215D0 (en) | 2004-05-05 |
EP1432893A1 (en) | 2004-06-30 |
WO2003029628A1 (en) | 2003-04-10 |
US6598400B2 (en) | 2003-07-29 |
GB2396661B (en) | 2005-08-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6598400B2 (en) | Gas turbine with articulated heat recovery heat exchanger | |
US5557922A (en) | Turbine | |
JP2675732B2 (en) | Combustion equipment | |
US6837419B2 (en) | Recuperator for use with turbine/turbo-alternator | |
CN102032047B (en) | For the apparatus and method of heat extraction from gas turbine | |
US8484975B2 (en) | Apparatus and method for start-up of a power plant | |
US20060037351A1 (en) | Cogeneration system and exhaust gas heat exchanger assembly thereof | |
US20070062175A1 (en) | Flexible flow control device for cogeneration ducting applications | |
RU2002123228A (en) | DEVICE FOR AIR CONDITIONING OF A TYPE OF HEAT PUMP WITH GAS AS A HEAT SOURCE, DEVICE FOR HEATING ENGINE WATER-COOLER AND METHOD OF OPERATION OF A DEVICE FOR AIR CONDITION OF UNIT OF HEAVY HEAVY HEATER | |
US20060037742A1 (en) | Cogeneration system | |
CA2578243A1 (en) | Configurations and methods for power generation with integrated lng regasification | |
JPH09503263A (en) | Cooling device for gas turbine cooling medium in gas / steam turbine complex | |
EP1628098A2 (en) | Cogeneration system | |
JPH1136889A (en) | Gas turbine cooler | |
JPH07208115A (en) | Method and equipment for operating gas turbine by combined cycle of simple cycle and steam turbine | |
WO2011151888A1 (en) | External-combustion, closed-cycle thermal engine | |
GB2034822A (en) | Gas turbine engine cooling air supply | |
EP0980495A1 (en) | An improved heat exchanger for operating with a combustion turbine in either a simple cycle or a combined cycle | |
US8033093B2 (en) | Gas turbine apparatus | |
US7954324B2 (en) | Gas turbine engine | |
US6499770B1 (en) | Flexible duct for a microturbine | |
CN105822427A (en) | Regenerative cycle gas turbine system and cooling, heating and power combined supply system | |
CZ2001995A3 (en) | System for compression and ejection of piston engines | |
US20050144931A1 (en) | Integral heat recovery device | |
EP0859135A1 (en) | Gas turbine with energy recovering |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: INGERSOLL-RAND ENERGY SYSTEMS CORPORATION, NEW HAM Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NASH, JAMES S.;KESSELI, JAMES B.;OLSEN, ANDREW J.;REEL/FRAME:012224/0780;SIGNING DATES FROM 20010911 TO 20010918 |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
AS | Assignment |
Owner name: SOUTHERN CALIFORNIA GAS COMPANY, CALIFORNIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:INGERSOLL-RAND ENERGY SYSTEMS CORPORATION;REEL/FRAME:020279/0715 Effective date: 20071220 |
|
FPAY | Fee payment |
Year of fee payment: 8 |
|
SULP | Surcharge for late payment |
Year of fee payment: 7 |
|
AS | Assignment |
Owner name: FLEXENERGY ENERGY SYSTEMS, INC., CALIFORNIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SOUTHERN CALIFORNIA GAS COMPANY;REEL/FRAME:033132/0476 Effective date: 20121001 |
|
REMI | Maintenance fee reminder mailed | ||
LAPS | Lapse for failure to pay maintenance fees | ||
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 20150729 |